Power rotated device for dispersing fluids into a gaseous environment

ABSTRACT

A device for dispersing fluids into a gaseous environment which includes a hollow body mounted for rotational movement about an axis of rotation by a motor or the like, the hollow body having a plurality of discharge orifices spaced circumferentially about the axis shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pattern which diverges outwardly with respect to a line of symmetry, the line of symmetry associated with each orifice being related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46* measured in any direction therefrom whereby dispersion of a source of fluid communicated with the inlet of the hollow body is distributed through the orifice into the surrounding gaseous medium under the action of both the pressure energy and kinetic energy developed during the operation of the device.

United States Patent [191 Johnson 1 June 5, 1973 [75] Inventor: William H. Johnson, Raleigh, NC.

[73] Assignee: Patent & Development of N.C., 1nc.,

Raleigh, NC.

[22] Filed: Sept. 17, 1971 [21] Appl.No.: 181,527

521 US. Cl ..239/225, 239/568 5 1 Int. Cl. ..B05b 3/00 581 Field of Search ..239/225, 251, 568

[56] References Cited UNITED STATES PATENTS 960,393 6/1910 Peters ..239/251 X 3,584,786 6/1971 Johnson ..239/568 1,776,714 9/1930 Armstrong ..239/25l 2,585,608 2/1952 Wieghart ..239/251 2,954,932 10/1960 Albano..- ..239/251 X 8/1971 Johnson ..239/251 Primary Examiner-Allen N. Knowles Att0rneyCushman, Darby & Cushman [5 7] ABSTRACT A device for dispersing fluids into a gaseous environment which includes a hollow body mounted for rotational movement about an axis of rotation by a motor or the like, the hollow body having a plurality of discharge orifices spaced circumferentially about the axis shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pat; tern which diverges outwardly with respect to a line of symmetry, the line of symmetry associated with each orifice being related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46 measured in any direction therefrom whereby dispersion of a source of fluid communicated with the inlet of the hollow body is distributed through the orifice into the surrounding gaseous medium under the action of both the pressure energy and kinetic energy developed during the operation of the device.

13 Claims, 5 Drawing Figures F2 0/17 Supp; Y

POWER ROTATED DEVICE FOR DISPERSING FLUIDS INTO A GASEOUS ENVIRONMENT This invention relates to the dispersion of fluids into a gaseous medium and more particularly to devices of this type which are operable to effect fine atomization of liquids into a gaseous medium.

Atomization of liquids refers to the formation of very fine droplets (generally less than 200 microns in diameter) through mechanical action or other means. During the process of atomization, the liquid is formed or dispersed into a thin film or sheet which is broken into fragments by frictional effects due to the difference in velocity between the liquid and the surrounding air. Surface tension also is a factor in the initial disruption of the film and in the formation of small droplets from the fragments.

In non-rotational devices, fine atomization is achieved by one or more of the following principles: (1) use of minute orifices to produce a small output, (2) wide-angle dispersion which effectively forms a thin film, (3 high pressures to obtain increased fluid discharge velocities, and (4) entrainment of the liquid in a high velocity medium. Single fluid, high pressure nozzles employ the first three principles and often use pressures up to 2000 lb/in to achieve atomization. This type is characterized by low capacity and complex, high pressure supply equipment. In a two-fluid device the liquid is atomized by entrainment and/or interaction with an inpinging stream of air or steam supplied at pressures up to 200 lb/in This type generally has less capacity than the single fluid, high pressure type. Both types deliver the atomized liquid into a rather restricted dispersion region.

In rotational devices, centrifugal forces are used to form a thin film on the surface of a disc or other structure. The centrifugal disc device uses a rotating disc of different designs driven at speeds up to 12,000 rpm. A similar design, called the inverted disc (hell or bowl shaped) operates on the same principle. Liquid is fed on to the center of the disc where it is evenly dispersed before being discharged from the periphery in the form of a fine spray. This type of device generally gives a higher capacity than non-rotational devices and has a low liquid input pressure requirement. Limitations to this design however include (1) restricted dispersion region (fluid discharged in essentially a flat plane) and (2) discharge velocity less than the tangential velocity due to inherent slippage. I A variant of the above type is the two-fluid, ring jet device which involves a combination of centrifugal force and an air blast. As liquid discharges from the periphery of the rotating disc, it is entrained in a high velocity blast of air from an air nozzle which surrounds the periphery of the disc and the fluid is torn into droplets. This method gives greater control of particle size, which is governed to a great extent byv the air supply pressure. However, it is rather complex involving twofluid operation and also has a restricted dispersion region.

The device of the present invention differs in both principle and performance from any of the previously described devices and combines certain atomization principles of both non-rotational and rotational types to achieve overall improvments with noted simplicity. These principles include 1) multiple, minute orifices for high discharge capacity, (2) wide-angle dispersion of fluid from discharge orifices, (3) high pressure fluid discharge, and (4) high rotational speed to achieve a high tangential velocity and a large dispersion region. Also of particular importance is the fact that high discharge pressures are developed by the rotating device and not required in the fluid supply. These pressures give wide-angle dispersion which, in rotation, establishes a considerably larger dispersion region than conventional devices of the prior art.

Accordingly it is an object of the present invention to provide a device of the type described which combines certain principles of both rotational and non-rotational devices to achieve improved atomization of liquids and controlled dispersion of either liquids or gases.

Another object of the present invention is to provide a device of the type described which utilizes both pressure and kinetic energies to achieve maximum exit fluid velocity and hence maximum frictional effects between the fluid and the surrounding air.

Another object of the present invention is to provide a device of the type described having improved atomization efficiency at a given rotational velocity, with higher fluid discharge velocities and larger regions of dispersion than comparable conventional rotary devices.

A further object of the present invention is to provide a device of the type described which utilizes centrifugal forces to develop a high fluid pressure at discharge orifices and as a result gives wide angle dispersion with exit velocities greater than maximum tangential velocity.

Another object of the present invention is to provide a device of the type described in which the fluid dispersion region can be easily varied to meet special requirements in the mixing of the discharged fluid into the surrounding medium.

A still further object of the present invention is to provide a device of the type described which does not require a high pressure fluid supply system, yet which is capable of high capacity with excellent atomization and has wide flexibility in volumetric capacity and degree of atomization.

A still further object of the present invention is the These and other objects of the present invention will become more apparent during the course of the following detailed description and appended claims.

The invention may best be understood with reference to the acompanying drawings wherein an illustrative embodiment is shown.

In the drawings:

FIG. 1 is a side elevational view of a device embodying the principles of the present invention, the device being shown partially broken away for the purposes of clearer illustration;

FIG. 2 is a reduced cross-sectional view taken along the line 2-2 of FIG. 1; 0

FIG. 3 is an enlarged fragmentary sectional view taken along the line 3-3 of FIG. 1;

FIG. 4 is an enlarged fragmentary sectional view taken along the line 4-4 of FIG. 1; and

FIG. 5 is a graph showing a family of curves by plotting the internal orifice pressures created at orifices spaced outwardly from the axis of rotation at various distances for representative rotational speeds of the device.

Referring now more particularly to the drawings, there is shown therein a device embodying the principles of the present invention. The device 10 comprises a hollow body, generally indicated at 12, having an axis of rotation which, in the embodiment shown, is disposed generally vertically so as to disperse a source of fluid, such as water or the like, into a gaseous environment surrounding the axis of rotation. The device 10 also includes power means for drivingly rotating the hollow body 12 about its axis of rotation which means in the preferred embodiment shown takes the form of an electrical motor 14. The device 10 in the preferred form is applicable in many installations involving atomization of liquids and controlled dispersion of fluids (either liquid or gas) into gaseous environments. These applications include humidification, fogging, spray drying combustion and numerous industrial processes. In this regard, it will be understood that the device has applicability with its axis of rotation disposed in positions other than the vertical position shown.

In the preferred embodiment shown in the drawings, the hollow body 12 is basically constructed of a hub assembly made up of two hub members 16 and 18 detachably fixedly secured together and a plurality of tubular structures, generally indicated at 20, detachably fixedly connected to the hub structure and extending generally radially outwardly therefrom in equally spaced circumferential relation. As shown, the hub member 16 includes a lower annular wall 22 having an imperforate end wall 24 extending radially inwardly from the upper end thereof. Formed integrally on the central portion of the upper surface of the end wall 24 is an integral boss or collar portion 26 which serves as a part of a driving connection means with the motor 14. As shown, the boss portion 26 is centrally apertured to snuggly receive therein an output shaft 28 of the electrical motor. A set screw 30 threadedly engaged within the boss portion 26 may be tightened into engagement with the periphery of the shaft 28 to complete the driving connection.

The lower interior surface of the annular wall 22 is threaded to receive a complementary exteriorly threaded upper end wall 32 of the hub member 18. The hub member 18 also includes an annular flange 34 extending radially outwardly of the end wall 32 which is suitably sealed with respect to the associated surface of the annular wall 22, as by a sealing gasket 36 or the like. In the embodiment shown, the hub member 18 includes a central depending lower end portion provided with exterior flat surfaces (not shown) to be engaged by a suitable tool to effect the assembly and disassembly of the two hub members.

Formed axially through the hub member 18 is an opening 38 constituting the inlet means of the hollow body 12 to which the source of fluid to be dispersed is communicated. It will be understood that the fluid source need not be under any initial pressure in which case a simple tube may be suitably engaged (e.g. by threads or the like) within the opening 38, the tube having a length sufficient to extend downwardly into the body of fluid such as a liquid confined within a container. It will also be understood that where the source of fluid is under pressure, such source can be communicated with the inlet 38 by a conventional rotary or swivel fitting and suitable conduit.

It is important to note, however, that a pressure-tight communication of the fluid source is not essential since the operation of the device produces a suction which will draw fluid from a source at atmospheric pressure into the inlet opening 38. It will also be understood that the device may be readily inverted so that the opening 38 is disposed above the motor 14, rather than below, as shown.

The inlet opening 38 communicates with a generally cylindrical shaped distribution cavity 40 defined by the interior surface of the annular wall 22 and the sub scribed interior surfaceof the end walls 24 and 32 of the hub members 16 and 18 respectively. The annular wall 22 is formed with a plurality of radially extending openings 42 equally spaced 'circumferenti'ally thereabout which communicate interiorly with the distribution cavity 40. In the embodiment shown, each opening 42 is interiorly threaded to receive a coupling assembly 44 of conventional construction, each of which serves to connect an associated tubular structure 20 within the associated opening 42 in interior communication with the distribution cavity 40.

In order to improve the flow characteristics of the fluid through the distribution cavity 40 radically outwardly to each of the coupling assemblies 44, the end wall 24 is formed with a depending conically shaped flow direction portion 46. In addition, the hub member 18 includes a plurality of flow directing vanes 48 which are integral with the end wall portion 32 and have a height substantially equal to the height of the cavity 40. As best shown in FIG. 3, the number of vanes provided is generally equal to the number of openings 42, the vanes being disposed angularly with respect to the openings so that their outer edges engage the inner surface of the annular wall 22 between the openings 42. The vanes 48 extend radially and have their inner edges disposed in spaced relation to the axis of rotation approximately at the outer edge of the conical portion 46.

The tubular structures 20 are formed with a series of discharge orifices 50, each of which is preferably constructed in accordance with the teachings of my U.S. Pat. No. 3,584,786, issued'June 15, 1971. In the preferred embodiment shown, each tubular structure 20 is formed from a generally straight cylindrical tube, one end of which may be suitably deformed in conventional fashion to cooperate with the coupling assembly 44. Each tube includes an outer end portion 52 bent in accordance with the teachings of my aforesaid patent into a configuration best shown in FIG. 4. As shown, each bent portion 52 provides a main longitudinally extending feed cavity 54 and a longitudinally communicating corona orifice cavity 56 provided by a forwardly projecting wing. The outer ends of the cavities 54 and 56 are suitably closed as by welding or the like. In the embodiment shown, a similar rearwardly'projecting wing is provided merely to render the tubular construction symmetrical and provide for both weight and aerodynamic balance. It will be understood that the rearwardly projecting wing may be eliminated if desired.

The corona orifice cavity 56 includes a smooth inner wall surface 58 of substantially semi-circular crosssectional configuration. In accordance with the teachings of my aforesaid patent, the surface 58 forms a near-perfect circular arc of about to about and has a diameter as small as 0.001 inch.

In the embodiment shown, each tube end portion 52 is provided with a plurality of orifices 50. Each orifice is formed by transversely slitting the wing defining the corona orifice cavity 56 in communication with the surface 58. In the embodiment shown, four orifices are formed in each tube end portion 52, the orifices being spaced equidistantly apart a distance considerably greater than the diameter of the arc of the surface 58. With this arrangement, fluid under pressure communicated interiorly with the corona orifice cavity 56 will discharge outwardly of each orifice 50 communicating therewith in a substantially flat fan-shaped pattern. The discharge from each orifice diverges outwardly from the orifice in the flat fan-shaped pattern with respect to a line of symmetry. in the embodiment shown, the line of symmetry of each orifice is coincident with a line extending through the associated orifice tangential to the axis of rotation of the hollow body 12.

As best shown in FIG. 2, the motor 14 is operable to drivingly rotate the hollow body about its axis of rotation in a direction corresponding to the outward extent of the aforesaid coincident lines of symmetry and tangential lines. The motor 14 is preferably rotated at a relatively high speed as, for example, from 1800 rpm to as high as 20,000 rpm and above. The advantages of the above described direction and speed of rotation will become apparent from the following description of the operation of the device and the general discussion of the operating principles involved.

Fine dispersion of fluids into a gaseous medium or environment is obtained in accordance with the principles of the present invention by providing for both wide angle and high velocity discharge through the discharge orifices 50. With respect to discharge velocities, maximum velocities are achieved in the operation of the preferred embodiment described above because of the additive effect obtained (1) by establishing a high discharge pressure due to the centrifugal forces imparted to the fluids adjacent the orifices because of the high rotational speed of the hollow body 12 and radial extent of fluid movement therethrough and (2) by establishing the direction of discharge, measured by the aforesaid line of symmetry, coincident with the direction of tangential velocity of each orifice 50.

The effect of fluid pressure on nozzle discharge velocity can be evaluated by considering Bernoullis equation for incompressible fluids A U /2g +(g/g AZ+AP/p= where U bulk velocity of the fluid, ft/sec; g, constant, 32.17 lb-ft/lb force-sec g acceleration of gravity, ft/sec; Z =height of fluid, ft; P total pressure, lbflft and p density, lb/ft.

For the same elevation (Z Z2). equation 1 becomes A Ul2g (A P/p),

or s a 8c (P1 z)/P Now assuming that the subscripts l and 2 refer to locations within and external to the nozzle orifice, re-

spectively U is small in comparison with U and P, 0. Under these conditions For water, equation 4 becomes Where P is the pressure expressed in psi. At a fluid pressure of psi the discharge velocity by equation 5 is 121.8 ft/sec. The higher the pressure, of course, the higher the discharge velocity.

Consider next the development of a fluid pressure as a result of centrifugal forces of rotation. The centrifugal forces dF exerted by the element of mass dm with constant radial acceleration, a, is

dF= a dm p (Vf/Xg dV where F force, lbf; a accelleration, ft/sec p density, lb/ft; V, tangential velocity, ft/sec; V volume, ft; X radius, ft; and g, 32.17 lb-ft/lbf-sec.

Replacing dV by AdX, where A is the cross-sectional area (ft), and V, by 21rX N, where N is revolutions/sec, equation 6 becomes Integrating over the length of the tube gives the total centrifugal force exerted on the outermost closed end,

F W 4L V f (ne I XdX, and

Dividing by A and inserting values for 1r, g and p, equation 8 becomes where P, is the pressure expressed in psi.

FIG. 5 shows graphically the results of equation 9 but with N expressed in rpm and L in inches. For example, at 5000 rpm, a rotating tube 9 inches long can develop a pressure which exceeds 1000 psi at the tip. At 20,000 rpm, a length of 2.2 inches will develop the same pressure.

The preferred radial tubular structures 20 provide in a single element (1) a means for supplying fluid to the desired discharge radius and (2) an optimum design for wide angle dispersion of fluid in the direction of rotation by means of orifices integral therein. It will be understood that, although the radial supply tubes as discussed are preferably straight and radially disposed, they may be curved or of other configuration providing they form suitable conduits for fluid flow which are capable of withstanding the centrifugal forces and supporting the developed fluid pressures. Furthermore the radial supply tubes may be varied in size, number, and

relationship to the dispersion hub assembly without departing from the stated principles of operation.

In the above discussion it is assumed that the fluid source is communicated with the inlet 38 under atmospheric pressure. It will be understood that where the fluid source is under a positive elevated pressure, this pressure less normal losses will likewise be added to the discharge pressure created by centrifugal force.

Of critical significance is the fact that, as aforesaid, the discharge velocity resulting from centrifugal forces is increased by the rotational velocity of the orifices since the direction of discharge in the preferred embodiment described is coincident with the instantaneous tangential direction of rotation. While this coincidence of direction is greatly preferred, some angular variation between the line of symmetry of each orifice with respect to a tangential line extending through the associated orifice is possible. An operative range in this regard is approximately 46 in any direction, a preferred range beinb 23 in any direction, with, of course, the preferred angular deviation being zero or coincidence as previously described.

The invention also contemplates the utilization of orifices having diverging discharge patterns other than the flat fan-shaped pattern achieved by the preferred orifice construction 50 as, for example, conical discharge orifices. Where the device is used to atomize liquid, the flat fan-shaped discharge pattern disposed with their flat surfaces parallel to the axis, is greatly preferred in that the fan action serves to dispel the gas eous medium immediately ahead of the rotating fan.

This action serves to increase the frictional effects between the liquid and the air, stretch the unbroken liquid film and improve atomization. Again, while orifices provided by transversely extending slits producing a flat fan-shaped discharge pattern having its flat surfaces parallel to the axis of rotation is preferred, it is within the contemplation of the present invention to vary the slit angle so that the flat surface of the fan-shaped discharge pattern is tilted or rotated about its line of symmetry. However, an excessive tilt angle, say 90, might well result in the formation of droplets adjacent the axis of rotation. Also excessive tilt will result in interference of one spray pattern with another in the case of multiple orifices and will concentrate the discharge fluid into a smaller region. Hence, the tendency toward the creation of such droplets adjacent the axis decreases as the position of the plane of the flat fan-shaped patterns approaches parallelism with the axis of rotation.

The capacity of the device 10 depends on several factors including the number and size of fluid supply tubes and orifices, length from the center of dispersion hub to orifices, rotational speed and fluid density and viscosity. High capacities are easily achieved with water as the supply fluid while still obtaining fine atomization. For example, where the tubular structures have a 10 inch dimension measured from the axis of rotation to the closed tip thereof and a 0.25 inch diameter and the motor 14 drives the tubular body 12 at a rotational speed of 5000 rpm, a pressure of approximately 1285 psi is developed within each tip producing a pressure velocity of 460 ft/sec which, combined with the rotational velocity of 436 ft/sec establishes a maximum discharge velocity of approximately 896 ft/sec.

It thus will be seen that the objects of this invention have been fully and effectively accomplished. It will be realized, however, that the foregoing preferred specific embodiment has been shown and described for the purpose of illustrating the functional and structural principles of this invention and is subject to change without departure from such principles. Therefore, this invention includes all modifications encompassed within the spirit and scope of the following claims.

What is claimed is:

l. A device for dispersing fluids into a gaseous environment comprising a hollow body having an axis of rotation, said body having a plurality of discharge orifices spaced circumferentially about said axis, each of said orifices being shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pattern which diverges outwardly with respect to a line of symmetry, each of said orifices being positioned so that said line of symmetry is related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46 measured in any direction therefrom, said body having inlet means for communicating a fluid source to the interior of said body at a position adjacent the axis thereof, and interior surface means for confining the fluid communicated with said inlet means to a flow path outwardly from said position adjacent said axis to said discharge orifices, and power means operatively connected with said body for imparting a rotational movement to said body about its axis in a direction corresponding to the outward extent of said tangential lines while said inlet means is communicated with a fluid source so that such fluid will flow outwardly of said discharge orifices with the combined energy resulting from the pressure and flow velocity of the fluid source into said inlet means, the pressure and flow velocity imparted to the fluid entering said inlet means by centrifugal force during the outward movement thereof along said interior flow path and the component of tangential velocity imparted to the fluid as it discharges from the orifices by the component of movement of the orifices in that direction.

2. A device as defined in claim 1 wherein said internal surface means adjacent each orifice extends in a smooth semi-cylindrical plane defining a corona orifice cavity slit transversely to provide the associated orifice from which the diverging discharge pattern is fan shapeds I 3. A device as defined in claim 2 wherein the transverse extent of each orifice providing slit is parallel to the rotational axis of said body so that the plane of each fan-shaped discharge pattern isparallel to the axis of rotation.

4. A device as defined in claim 3 wherein the angle between each of said tangential lines and the associated line of symmetry is less than 23.

5. A device as defined in claim 4 wherein each of said tangential lines coincides with the associated line of symmetry.

6. A device as defined in claim 1 wherein said body includes a hub assembly providing an annular wall having a plurality of circumferentially spaced openings therein, a plurality of elongated tubular parts each having an inner end thereof sealingly connected in communicating relation with an opening and extending outwardly therefrom, the outer end portion of each tubular part being closed, said orifices being disposed in the closed outer end portions of said tubular parts.

7. A device as defined in claim 6 wherein each of said tubular parts comprises a thin walled tube having a main longitudinally extending feed cavity, the outer end portion of said tube being formed to provide a longitudinally extending corona discharge wing projecting forwardly with respect to the direction of rotation, said wing defining a corona orifice cavity having a smooth inner wall surface constituting a part of said interior surface means which is substantially semicircular in cross-sectional configuration, at least one of said orifices being formed in said wing by slitting the corona orifice cavity transversely through said inner wall surface.

8. A device as defined in claim 7 wherein said inner wall surface of semi-circular cross-sectional configuration has a diameter of the order of .001 inches.

9. A device as defined in claim 8 wherein each of said wings is formed with a plurality of said orifices by slitting as aforesaid at locations spaced longitudinally therealong a spacing distance greater than said surface diameter.

10. A device as defined in claim 9 wherein each of said tangential lines coincides with the associated line of symmetry and wherein the tranverse extent of each orifice providing slit is within a plane coincident with the associated tangential line and parallel with the rotational axis of said body.

11. A device as defined in claim 6 wherein said hub assembly includes opposed end walls extending inwardly from opposite axial ends of said annular wall, said inlet means being formed axially in one of said end walls, the opposite end wall having a generally conically shaped flow directing axial portion disposed in opposed relation to said inlet means.

12. A device as defined in claim 11 wherein said hub assembly includes a plurality of circumferentially spaced vanes extending from said annular wall at positions between the openings therein radially inwardly between said end walls and terminating in spaced relation to the axis of rotation.

13. A method of dispersing fluids into a gaseous environment with the use of a hollow body having an axis of rotation, fluid inlet means adjacent the axis thereof and a plurality of circumferentially spaced discharge orifices, each of which is shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pattern which diverges outwardly with respect to a line of symmetry and is positioned so that the line of symmetry is related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46 measured in any direction therefrom, said method comprising the steps of communicating a fluid source with the fluid inlet means of said hollow body and imparting a rotational movement to said body about its'axis in a direction corresponding to the outward extent of the aforesaid tangential lines at a speed greater than approximately 1800 rpm sufficient fo cause the fluid source to flow outwardly of the discharge orifices with the combined energy resulting from the pressure and flow velocity of the fluid source into the inlet means, the pressure and flow velocity imparted to the fluid entering the inlet means by centrifugal force during the outward movement thereof toward said discharge orifices and the component of tangential velocity imparted to the fluid as it discharges from the orifices by the component of movement of the orifices in that direction. 

1. A device for dispersing fluids into a gaseous environment comprising a hollow body having an axis of rotation, said body having a plurality of discharge orifices spaced circumferentially about said axis, each of said orifices being shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pattern which diverges outwardly with respect to a line of symmetry, each of said orifices being positioned so that said line of symmetry is related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46* measured in any direction therefrom, said body having inlet means for communicating a fluid source to the interior of said body at a position adjacent the axis thereof, and interior surface means for confining the fluid communicated with said inlet means to a flow path outwardly from said position adjacent said axis to said discharge orifices, and power means operatively connected with said body for imparting a rotational movement to said body about its axis in a direction corresponding to the outward extent of said tangential lines while said inlet means is communicated with a fluid source so that such fluid will flow outwardly of said discharge orifices with the combined energy resulting from the pressure and flow velocity of the fluid source into said inlet means, the pressure and flow velocity imparted to the fluid entering said inlet means by centrifugal force during the outward movement thereof along said interior flow path and the component of tangential velocity imparted to the fluid as it discharges from the orifices by the component of movement of the orifices in that direction.
 2. A device as defined in claim 1 wherein said internal surface means adjacent each orifice extends in a smooth semi-cylindrical plane defining a corona orifice cavity slit transversely to provide the associated orifice from which the diverging discharge pattern iS fan shaped.
 3. A device as defined in claim 2 wherein the transverse extent of each orifice providing slit is parallel to the rotational axis of said body so that the plane of each fan-shaped discharge pattern is parallel to the axis of rotation.
 4. A device as defined in claim 3 wherein the angle between each of said tangential lines and the associated line of symmetry is less than 23*.
 5. A device as defined in claim 4 wherein each of said tangential lines coincides with the associated line of symmetry.
 6. A device as defined in claim 1 wherein said body includes a hub assembly providing an annular wall having a plurality of circumferentially spaced openings therein, a plurality of elongated tubular parts each having an inner end thereof sealingly connected in communicating relation with an opening and extending outwardly therefrom, the outer end portion of each tubular part being closed, said orifices being disposed in the closed outer end portions of said tubular parts.
 7. A device as defined in claim 6 wherein each of said tubular parts comprises a thin walled tube having a main longitudinally extending feed cavity, the outer end portion of said tube being formed to provide a longitudinally extending corona discharge wing projecting forwardly with respect to the direction of rotation, said wing defining a corona orifice cavity having a smooth inner wall surface constituting a part of said interior surface means which is substantially semicircular in cross-sectional configuration, at least one of said orifices being formed in said wing by slitting the corona orifice cavity transversely through said inner wall surface.
 8. A device as defined in claim 7 wherein said inner wall surface of semi-circular cross-sectional configuration has a diameter of the order of .001 inches.
 9. A device as defined in claim 8 wherein each of said wings is formed with a plurality of said orifices by slitting as aforesaid at locations spaced longitudinally therealong a spacing distance greater than said surface diameter.
 10. A device as defined in claim 9 wherein each of said tangential lines coincides with the associated line of symmetry and wherein the tranverse extent of each orifice providing slit is within a plane coincident with the associated tangential line and parallel with the rotational axis of said body.
 11. A device as defined in claim 6 wherein said hub assembly includes opposed end walls extending inwardly from opposite axial ends of said annular wall, said inlet means being formed axially in one of said end walls, the opposite end wall having a generally conically shaped flow directing axial portion disposed in opposed relation to said inlet means.
 12. A device as defined in claim 11 wherein said hub assembly includes a plurality of circumferentially spaced vanes extending from said annular wall at positions between the openings therein radially inwardly between said end walls and terminating in spaced relation to the axis of rotation.
 13. A method of dispersing fluids into a gaseous environment with the use of a hollow body having an axis of rotation, fluid inlet means adjacent the axis thereof and a plurality of circumferentially spaced discharge orifices, each of which is shaped to disperse fluid under pressure communicated interiorly therewith outwardly thereof in a pattern which diverges outwardly with respect to a line of symmetry and is positioned so that the line of symmetry is related to a line tangential to the axis of rotation intersecting the associated orifice by an angle of less than 46* measured in any direction therefrom, said method comprising the steps of communicating a fluid source with the fluid inlet means of said hollow body and imparting a rotational movement to said body about its axis in a direction corresponding to the outward extent of the aforesaid tangential lines at a speed greater than approximately 1800 rpm sufficient fo cause the fluid source to flow outwardly of the discharge orifices with the combined energy resulting from the pressure and flow velocity of the fluid source into the inlet means, the pressure and flow velocity imparted to the fluid entering the inlet means by centrifugal force during the outward movement thereof toward said discharge orifices and the component of tangential velocity imparted to the fluid as it discharges from the orifices by the component of movement of the orifices in that direction. 